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WO2008105760A2 - Évaporateur à tube plat multicanaux avec évacuation de condensat améliorée - Google Patents

Évaporateur à tube plat multicanaux avec évacuation de condensat améliorée Download PDF

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Publication number
WO2008105760A2
WO2008105760A2 PCT/US2007/004993 US2007004993W WO2008105760A2 WO 2008105760 A2 WO2008105760 A2 WO 2008105760A2 US 2007004993 W US2007004993 W US 2007004993W WO 2008105760 A2 WO2008105760 A2 WO 2008105760A2
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchange
recited
flattened
condensate drain
heat exchanger
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/US2007/004993
Other languages
English (en)
Other versions
WO2008105760A3 (fr
Inventor
Michael F. Taras
Alexander Lifson
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carrier Corp
Original Assignee
Carrier Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Carrier Corp filed Critical Carrier Corp
Priority to PCT/US2007/004993 priority Critical patent/WO2008105760A2/fr
Priority to US12/527,779 priority patent/US8307669B2/en
Priority to HK10107500.6A priority patent/HK1141078B/xx
Priority to CN2007800526833A priority patent/CN101657689B/zh
Priority to EP07751730A priority patent/EP2122289A4/fr
Publication of WO2008105760A2 publication Critical patent/WO2008105760A2/fr
Publication of WO2008105760A3 publication Critical patent/WO2008105760A3/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0471—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D2001/0253—Particular components
    • F28D2001/026—Cores
    • F28D2001/0273—Cores having special shape, e.g. curved, annular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators

Definitions

  • This invention relates generally to refrigerant vapor compression system heat exchangers having a plurality of parallel, flat heat exchange tubes extending between a first header and a second header with heat transfer fins positioned between these tubes, and more particularly, to providing for improved drainage of condensate collecting on the external surfaces of these flat tubes and fins.
  • Air conditioners and heat pumps employing refrigerant vapor compression cycles are commonly used for cooling or cooling/heating air supplied to a climate controlled comfort zone within a residence, office building, hospital, school, restaurant or other facility.
  • Refrigerant vapor compression systems are also commonly used for cooling air, or other secondary media such as water or glycol solution, to provide a refrigerated environment for food items and beverage products within display cases, bottle coolers or other similar equipment in supermarkets, convenience stores, groceries, cafeterias, restaurants and other food service establishments.
  • these refrigerant vapor compression systems include a compressor, a condenser, an expansion device, and an evaporator serially connected in refrigerant flow communication.
  • the aforementioned basic refrigerant vapor compression system components are interconnected by refrigerant lines in a closed refrigerant circuit and arranged in accord with the vapor compression cycle employed.
  • the expansion device commonly an expansion valve or a fixed-bore metering device, such as an orifice or a capillary tube, is disposed in the refrigerant line at a location in the refrigerant circuit upstream, with respect to refrigerant flow, of the evaporator and downstream of the condenser.
  • the expansion device operates to expand the liquid refrigerant passing through the refrigerant line, connecting the condenser to the evaporator, to a lower pressure and temperature.
  • the refrigerant vapor compression system may be charged with any of a variety of refrigerants, including, for example, R-12, R-22, R-134a, R-404A, R-410A, R-407C, R717, R744 or other compressible fluid.
  • the evaporator is a parallel tube heat exchanger having a plurality of flat, typically rectangular or oval in cross-section, multi-channel tubes extending longitudinally in parallel, spaced relationship between a first generally vertically extending header or manifold and a second generally vertically extending header or manifold, one of which serves as an inlet header/manifold.
  • the inlet header receives the refrigerant flow from the refrigerant circuit and distributes this refrigerant flow amongst the plurality of parallel flow paths through the heat exchanger.
  • the other header serves to collect the refrigerant flow as it leaves the respective flow paths and to direct the collected flow back to the refrigerant line to return to the compressor in a single pass heat exchanger, which in this case, serves as an outlet header/manifold, or to a downstream bank of parallel heat exchange tubes in a multi-pass heat exchanger.
  • this header is an intermediate manifold or a manifold chamber and serves as an inlet header to the next downstream bank of parallel heat transfer tubes.
  • Each multi-channel tube generally has a plurality of flow channels extending longitudinally in parallel relationship the entire length of the tube, each channel providing a relatively small flow area refrigerant flow path.
  • a heat exchanger with multi-channel tubes extending in parallel relationship between the inlet and outlet headers of the heat exchanger will have a relatively large number of small flow area refrigerant flow paths extending between the two headers.
  • multi-channel heat exchanger constructions are called microchannel or minichannel heat exchangers as well.
  • the heat exchanger generally includes heat transfer fins positioned between heat transfer tubes for heat transfer enhancement, structural rigidity and heat exchanger design compactness. The heat transfer tubes and fins are permanently attached to each other (as well as to the manifolds) during a furnace braze operation.
  • the fins may have flat, wavy, corrugated or louvered design and typically form triangular, rectangular, offset or trapezoidal airflow passages.
  • moistu ⁇ e in the air flowing through the evaporator and over the external surfaces of the refrigerant conveying tubes and associated fins of the heat exchanger condenses out of the air and collects on the external surface of the those tubes and fins.
  • condensate naturally drains well from refrigerant vapor compression system evaporators having round heat transfer tubes and plate fins due to the cylindrical outer surface of a round tube and vertically extended plate fins.
  • the condensate depositing on the heat transfer tubes and associated heat transfer fins inherently drains down the vertically extending tubes under the influence of gravity.
  • the draining condensate is typically collected in a drain pan disposed beneath the heat exchanger.
  • U.S. Patent No. 5,279,360 discloses an evaporator heat exchanger having an array of parallel heat exchange tubes of flattened cross-section disposed in spaced relationship with V-shaped fins disposed between the facing flat surfaces of adjacent heat exchange tubes.
  • Each heat exchange tube is bent into a V-shape and disposed in a vertical plane with its inlet end connected in fluid communication with a first horizontally extending header and its outlet end connected in fluid communication with a second horizontally extending header.
  • the apexes of the arrayed V-shape-bent heat exchange tubes are aligned at a lower elevation than the headers, and a condensate trough is disposed therebeneath. Condensate collecting on the flattened heat exchange tubes and the fins therebetween drains downwardly along the respective fin-free edge surfaces of the flattened heat exchange tubes to the condensate trough.
  • condensate collecting on the external surfaces of the heat transfer tubes of the evaporator may be undesirability re-entrained in the air passing through the evaporator and transversely over the flattened tubes. Further, under certain conditions, excessive condensate retention promotes faster frost accumulation and undesirably requires more frequent defrost cycles.
  • a heat exchange tube in an aspect of the invention, includes a tubular member having a flattened cross-section and extending along a longitudinal axis, and a longitudinally extending condensate drain channel formed in an upper wall of said flattened tubular member.
  • the tubular member has an upper wall and a lower wall defining at least one longitudinally extending fluid flow passage therebetween, a leading edge and a trailing edge.
  • the condensate drain channel may extend along a longitudinal axis positioned centrally between the leading edge and the trailing edge of the flattened tubular member, or along a longitudinal axis positioned closer to the leading edge than the trailing edge of the flattened tubular member, or along a longitudinal axis positioned closer to the trailing edge than the leading edge of the flattened tubular member.
  • the condensate drain channel formed in the upper external surface of the upper wall of the flattened tubular member may extend downwardly the full height of the fluid flow passage or less than the height of the fluid flow passage.
  • a heat exchanger for cooling a flow of air passing therethrough includes a first and a second spaced apart and generally vertical longitudinally extending headers; a plurality of heat exchange tubes disposed in parallel, spaced relationship in a generally vertical array and extending longitudinally between the first header and the second header, each of the heat exchange tubes having a longitudinal axis, a flattened cross-section, an upper wall and a lower wall defining at least one longitudinally extending fluid flow passage in fluid communication between the headers; and a condensate drain extending longitudinally along the upper wall of at least one of the plurality of flattened heat exchange tubes.
  • the condensate drain comprises a longitudinally extending condensate drain channel formed in the upper wall of at least one of the plurality of flattened heat exchange tubes.
  • the condensate drain channel may extend along a longitudinal axis positioned centrally between the leading edge and the trailing edge of the flattened tubular member, or along a longitudinal axis positioned closer to the leading edge than the trailing edge of the flattened tubular member, or along a longitudinal axis positioned closer to the trailing edge than the leading edge of the flattened tubular member.
  • the condensate drain channel formed in the upper external surface of the upper wall of the flattened tubular member may extend downwardly the full height of the fluid flow passage or less than the height of the fluid flow passage.
  • the heat exchanger may include a plurality of heat transfer fins extending between adjacent heat exchange tubes of the parallel tube array.
  • the condensate drain comprises at least one condensate drain portal formed in each fin of the plurality of fins in a base portion bounding the upper external surface of at least one heat exchange tube.
  • the condensate drain portals of neighboring fins are aligned longitudinally, thereby providing a series of longitudinally aligned condensate drain portals along the upper external surface of the heat exchange tube.
  • the condensate drain portals may be aligned to extend along a longitudinal axis positioned centrally between the leading edge and the trailing edge of the flattened tubular member, or along a longitudinal axis positioned closer to the leading edge than the trailing edge of the flattened tubular member, or along a longitudinal axis positioned closer to the trailing edge than the leading edge of the flattened tubular member.
  • a series of longitudinally aligned condensate drain portals pass through the fins superadjacent a longitudinally extending condensate drain channel formed in the upper wall of the heat exchange tube against which the base of the fins abuts.
  • the heat exchange tubes may be disposed at a slight angle of declination with the horizontal to allow gravity to enhance the drainage of condensate along the longitudinally extending condensate drains.
  • the heat transfer tubes may be formed in the shape of an inverted- V. In an embodiment, the heat transfer tubes may be formed in the shape of an arch.
  • each flattened heat exchange tube defines a plurality of parallel fluid flow paths extending parallel to a longitudinal axis thereof, with each fluid flow path of the plurality of parallel fluid flow paths having an inlet to the fluid flow path opening in fluid communication to the first header and an outlet to the fluid flow path opening in fluid communication to the second header.
  • the plurality of the channels defining the flow paths within each heat transfer tube may be, for instance, of circular, oval, rectangular, triangular or trapezoidal cross-section.
  • each of the fluid flow paths may comprise a refrigerant flow path.
  • FIG. 1 is a schematic diagram of a refrigerant vapor compression system incorporating a flat tube heat exchanger as an evaporator;
  • FIG. 2 is a perspective view of an exemplary embodiment of a flat tube evaporator heat exchanger in accordance with the invention
  • FIGs. 3A-3E are partially sectioned, elevation views of various exemplary embodiments of a flattened heat exchange tube including a condensate drain channel;
  • FIGs. 4A-4D are partially sectioned, elevation views of various embodiments of a flat tube heat exchanger including condensate drain portals;
  • FIG. 5 is a partially sectioned, elevation view of an exemplary embodiment of a flat tube heat exchanger having both condensate drain channels and condensate drain portals;
  • FIG. 6 is an elevation view of another exemplary embodiment of a flat tube heat exchanger having condensate drains;
  • FIG. 7 is an elevation view of another exemplary embodiment of a flat tube heat exchanger having condensate drains;
  • FIG. 8 is an elevation view of another exemplary embodiment of a flat tube heat exchanger having condensate drains
  • FIG. 9 is an elevation view of another exemplary embodiment of a flat tube heat exchanger having condensate drains
  • FIG. 10 is an elevation view of another exemplary embodiment of a flat tube heat exchanger having condensate drains.
  • FIG. 11 is an elevation view of another exemplary embodiment of a flat tube heat exchanger having condensate drains.
  • the heat exchanger of the invention will be described herein in use as an evaporator in connection with a simplified air conditioning cycle refrigerant vapor compression system 100 as depicted schematically in FIG. 1.
  • a simplified air conditioning cycle refrigerant vapor compression cycle illustrated in FIG. 1 is a simplified air conditioning cycle
  • the heat exchanger of the invention may be employed in refrigerant vapor compression systems of various designs, including, without limitation, heat pump cycles, economized cycles, cycles with tandem components such as compressors and heat exchangers, chiller cycles, cycles with reheat, subcritical cycles, supercritical cycles, and many other cycles including various options and features.
  • the system 110 will be described herein within a subcritical application.
  • the refrigerant vapor compression system 100 includes a compressor 105, a condenser 110, an expansion device 120, and the heat exchanger 10, functioning as an evaporator, connected in a closed loop refrigerant circuit by refrigerant lines 102, 104 and 106.
  • the heat exchanger 1 10 would function as a gas cooler, rather than a condenser.
  • the compressor 105 circulates hot, high pressure refrigerant vapor through discharge refrigerant line 102 into the inlet header of the condenser 110, and thence through the heat exchanger tubes of the condenser 110 wherein the hot refrigerant vapor is desuperheated, condensed to a liquid and typically subcooled as it passes in heat exchange relationship with a cooling fluid, such as ambient air, which is passed over the heat exchange tubes of the condenser by the condenser fan 115.
  • a cooling fluid such as ambient air
  • the high pressure refrigerant leaves the condenser (the gas cooler, in supercritical applications) 110 and thence passes through the refrigerant line 104 to the evaporator heat exchanger 10, traversing the expansion device 120 wherein the refrigerant is expanded to a lower pressure and temperature to form a refrigerant liquid/vapor mixture.
  • the now lower pressure and lower temperature, expanded refrigerant passes through the heat exchange tubes 40 of the evaporator heat exchanger 10 wherein the refrigerant is evaporated and typically superheated as it passes in heat exchange relationship with air to be cooled (and, in many cases, dehumidified), which is passed over the heat exchange tubes 40 and associated heat transfer fins 50 by the evaporator fan 15.
  • the refrigerant leaves the evaporator heat exchanger 10 predominantly in a vapor thermodynamic state and passes therefrom through the suction refrigerant line 106 to return to the compressor 105 through the suction port.
  • the air flow traversing the evaporator heat exchanger 10 passes over the heat exchange tubes 40 and heat transfer fins 50 in heat exchange relationship with the refrigerant flowing through the heat exchange tubes 40, the air is cooled and the moisture in the air flowing through the evaporator heat exchanger 10 and over the external surface of the refrigerant conveying tubes 40 and heat transfer fins 50 of the evaporator heat exchanger 10 condenses out of the air and collects of the external surfaces of the heat exchange tubes 40 and heat transfer fins 50.
  • a drain pan 45 is provided beneath the evaporator heat exchanger 10 for collecting condensate that drains from the external surface of the heat exchange tubes 40 and associated heat transfer fins 50.
  • the parallel flow heat exchanger 10 includes a plurality of heat exchange tubes 40 that are arranged in a generally vertical array. Iri the exemplary embodiment of the heat exchanger 10 depicted in FIG. 2, each of the heat exchange tubes 40 extends in a horizontal direction along its longitudinal axis between a generally vertically extending first header 20 and a generally vertically extending second header 30, thereby providing a plurality of parallel refrigerant flow paths between the two headers.
  • the refrigerant headers 20 and 30 are shown of a cylindrical configuration, the may be of a rectangular, half of cylinder or any other shape as well as have a single chamber or multi-chamber design, depending on the refrigerant path arrangement.
  • Each heat exchange tube 40 has a first end mounted to the first header 20, a second end mounted to the second header 30, and at least one flow channel 42 extending longitudinally, i.e. parallel to the longitudinal axis of the tube for the entire length of the tube, thereby providing a flow path in refrigerant flow communication between the first header and the second header.
  • the internal refrigerant pass arrangement may be a multi-pass configuration, such as depicted in FIG. 2, or a single-pass configuration, depending on particular application requirements.
  • each heat exchange tube 40 comprises an elongated tubular member 44 extending along its longitudinal axis and having a generally flattened cross-section, for example, a rectangular cross-section or oval cross-section.
  • the flattened tubular member has an upper wall 46 and a lower wall 48 and defines the at least one longitudinally extending fluid flow passage 42.
  • the at least one fluid flow passage 42 may be subdivided into a plurality of parallel, independent fluid flow passages 42 which extend longitudinally parallel to the longitudinal axis of the tubular member 44 in a side-by-side array, thereby providing a multi-channel heat exchange tube of better performance and structural rigidity.
  • Each flattened tubular member 44 has a leading edge 41 which faces upstream, with respect to airflow passing through the heat exchanger 10, and a trailing edge 43, which faces downstream, with respect to air flow passing through the heat exchanger 10.
  • Each flattened multi-channel tube 40 may have a width as measured along a transverse axis extending from the leading edge 41 to the trailing edge 43 of, for example, fifty millimeters or less, typically from ten to thirty millimeters, and a height of about two millimeters or less, as compared to conventional prior art round tubes having a diameter of 1/2 inch, 3/8 inch or 7 mm.
  • the heat exchange tubes 40 are shown in the accompanying drawings, for ease and clarity of illustration, as having ten channels 42 defining flow paths having a rectangular cross-section. However, it is to be understood that in applications, each multi-channel heat exchange tube 40 may typically have from about ten to about twenty flow channels 42.
  • each flow channel 42 will have a hydraulic diameter, defined as four times the cross-sectional flow area divided by the "wetted" perimeter, in the range generally from about 200 microns to about 3 millimeters.
  • the channels 42 may have a circular, triangular, oval or trapezoidal cross-section, or any other desired non- circular cross-section.
  • heat transfer tubes 40 may have other internal heat transfer enhancement elements, such as mixers and boundary layer destructors.
  • the heat exchanger 10 includes a plurality of external heat transfer fins 50 extending between each set of the parallel-arrayed tubes 40.
  • the fins are brazed or otherwise securely attached to the external surfaces of the upper and lower walls of the respective tubular members 44 of adjacent tubes 40 to establish heat transfer contact, by heat conduction, between the fins 50 and the external surfaces of the flat heat transfer tubes 40.
  • the external surfaces of the tubular members 44 of the heat transfer tubes 40 and the surfaces of the fins 50 together form the external heat transfer surface that participates in heat transfer interaction with the air flowing through the heat exchanger 10.
  • the external heat transfer fins 50 also provide for structural rigidity of the heat exchanger 10 and quite often assist in air flow redirection to improve heat transfer characteristics.
  • the fins 50 constitute segments of a fin strip formed as a serpentine series of generally V-shaped or generally U-shaped segments and disposed between and in heat transfer contact with the lower external surface of the lower wall 48 of one heat exchange tube 40 and the upper external surface of the upper wall 46 of the adjacent heat exchange tube 40 positioned next therebelow.
  • the fins may constitute a plurality of plates disposed in parallel, spaced relationship and extending generally vertically between the heat transfer tubes 40. It is to be understood that other fin configurations, such as, for example, generally corrugated, wavy, louvered or offset fins forming triangula ⁇ , rectangular, or trapezoidal airflow passages may be used in the heat exchanger 10 of the invention.
  • a heat exchanger used as an evaporator in refrigerant vapor compression system such as, for example, but not limited to, an air conditioning system, are subject to water condensing out of the air flow passing through the evaporator and collecting on the external surfaces of the heat exchange tubes 40 of the heat exchanger 10.
  • a condensate drain 65 is provided in association with at least one of the heat exchange tubes 40 to facilitate drainage of the collected condensate therefrom.
  • the condensate drain extends longitudinally along the upper external surface of the upper wall 46 of the flattened tubular member 44 of the heat exchange tube 40.
  • the condensate drain 65 may comprise a longitudinally extending condensate drain channel 65A formed in the upper external surface of the upper wall 46 of the flattened tubular member 44 of the heat exchange tube 40 and/or a series of condensate drain portals 65B formed in the fins 50 in the base portion thereof abutting the upper external surface of the upper wall 46 of the flattened tubular member 44 of the heat exchange tube 40.
  • a longitudinally extending condensate drain channel 65 A may be provided in the upper wall 46 of the flattened tubular member 44 of the heat exchange tube 40.
  • the condensate drain channel 65 A may extend along a longitudinal axis positioned centrally between the leading edge 41 and the trailing edge 43 of the flattened tubular member 44 as illustrated in FIG. 3 A, or along a longitudinal axis positioned closer to the leading edge 41 than to the trailing edge 43 of the flattened tubular member 44 as illustrated in FIG 3B, or along a longitudinal axis positioned closer to the trailing edge 43 than to the leading edge 41 of the flattened tubular member 44 as illustrated in FIG 3C. Further, more than one condensate drain channel 65A may be provided in the upper wall 46 of the heat exchange tube 40.
  • a pair of condensate drain channels 65 A may be formed in the upper wall 46 of the heat exchange tube 40 in transversely spaced relationship as illustrated in FIG. 3D.
  • the condensate drain channels may be formed in the upper wall 46 of the heat transfer tube 40 by crimping or by extrusion during the manufacturing of the heat exchange tube 40.
  • the depth of the condensate drain channel 65 A may extend the full height of the interior of the tubular member 44 such that the inside surface of the upper wall 46 at the apex of the channel 65 A touches the inside surface of the lower wall 48 of the tubular member 44.
  • the depth of the condensate drain channel 65 A may extend only partially across the interior of the tubular member 44 such that the inside surface of the upper wall of the channel 65 A does not touch the inside surface of the lower wall 48 of the tubular member 44. Also, the depth of the condensate drain channel 65 A may vary along the longitudinal extent of the channel 65 A, such as illustrated in FIG. 3E, so as to enhance drainage of condensate along the channel 65 A towards an outer end or ends of the tubular member 44.
  • the condensate drain channels 65A may be of any cross-section suitable for manufacturing, and in particular, of triangular, rectangular, square, trapezoidal, circular, oval or any other cross-section.
  • a series of condensate drain portals 65B are formed in the heat transfer fins 50, such as, for example, but not limited to, stamping or cutting, in the base portion thereof abutting the upper wall 46 of the flattened tubular member 44 of the heat exchange tube 40.
  • the condensate drain portals 65B may extend along a longitudinal axis positioned centrally between the leading edge 41 and the trailing edge 43 of the flattened tubular member 44 as illustrated in FIG.
  • FIG 4A or along a longitudinal axis positioned closer to the leading edge 41 than to the trailing edge 43 of the flattened tubular member 44 as illustrated in FIG 4B, or along a longitudinal axis positioned closer to the trailing edge 43 than to the leading edge 41 of the flattened tubular member 44 as illustrated in FIG 4C.
  • more than one condensate drain portal 65B may be provided in each of the heat transfer fins 50.
  • a first series of aligned portals 65B may be formed in the heat transfer fins 50 extending along a first longitudinal line and a second series of aligned portals 65B may be formed in the heat transfer fins 50 extending along a second longitudinal line disposed in transversely spaced relationship with the first longitudinal line of portals in the heat transfer fins 50, as illustrated in FIG.4D.
  • the condensate drain portals 65B may be aligned along a longitudinally extending so as to provide a path by which condensate collecting on the upper external surfaces of the heat exchange tube 40 against which the base of the heat transfer fins 50 abut in the heat exchanger 10. In an embodiment, as illustrated FIG.
  • the condensate drain may include both a condensate drain passage 65 A and a corresponding series of condensate drain portals 65B wherein a series of condensate drain portals formed in the heat transfer fins 50 are aligned along a longitudinal line co-linear with a longitudinal line along which a condensate drain channel 65A is formed in the upper wall 46 of the flattened upper member 44 against which the fins 50 abut.
  • the condensate drain portals 65B may be of any cross-section suitable for manufacturing, and in particular, of triangular, rectangular, square, trapezoidal, circular, oval or any other cross-section.
  • the entire heat exchanger 10 may be tilted slightly with respect to the horizontal and vertical to provide a downhill tilt to the condensate drains extending longitudinally along the upper external surface of the flattened tubular members 44, thereby allowing for gravity to assist in the drainage of condensate along the condensate drain channels and portals.
  • the headers 20 and 30 are no longer directly vertically extending, but rather extend generally vertically, that is at a slight angle to the vertical.
  • the heat exchange tubes 40 do no longer extend directly horizontally, but rather extend generally horizontally, that is at slight angle to the horizontal.
  • An angle of declination of at least 5 degrees, and generally in the range of at least 5 degrees to about 10 degrees, will be sufficient to enhance drainage of condensate along the condensate drains, whether channels or portals.
  • the heat exchange tubes 40 may be disposed at a slight angle of declination with the horizontal, while maintaining the headers 20 and 30 extending directly vertically, such as, for example, illustrated in the various embodiments of the heat exchanger 10 depicted in FIGs. 7-11.
  • the inlet and outlet ends of the heat exchange tubes are offset relative to the headers 20 and 30, whereby a substantial portion (FIG. 7) or the entire length (FIG.
  • each of the heat exchange tubes 40 has a generally inverted V-shape with the center of the tube at the apex of the inverted-V and the respective ends of the tube disposed at a lower elevation.
  • each of the left and right sections of each heat exchange tube 40 extend longitudinally from the center of the tube at a angle of declination to the horizontal thereby enhancing the drainage of condensate from the center to both the left and the right along the condensate drain.
  • the included angle at the apex of the inverted-V should be less than 170 degrees and may generally be in the range of from about 160 degrees to less than 170 degrees, whereby the left and right sections of the heat exchange tube 40 will extend longitudinally away from the center of the tube at an angle of declination of at least 5 degrees.
  • each of the heat exchange tubes 40 has an arch-like shape with the center of the tube at the apex of the arch and the respective ends of the tube disposed at a lower elevation.
  • the each of the left and right sections of each heat exchange tube 40 again extend longitudinally from the center of the tube at a angle of declination to the horizontal thereby enhancing the drainage of condensate from the center to both the left and the right along the condensate drains.
  • an angle of declination of at least 5 degrees, and generally in the range of at least 5 degrees to about 10 degrees, will be sufficient to enhance drainage of condensate along the condensate drains, whether channels or portals.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

Un tube d'échangeur de chaleur comprend un élément tubulaire présentant une section transversale aplatie et s'étendant le long d'un axe longitudinal, et un canal d'évacuation de condensat s'étendant longitudinalement formé dans une paroi supérieure de l'élément tubulaire aplati. Un échangeur de chaleur comprend un premier et un second collecteur espacés l'un de l'autre et s'étendant longitudinalement de manière globalement verticale, une pluralité de tubes d'échange de chaleur disposés parallèlement et espacés les uns des autres dans un ensemble globalement vertical et s'étendant longitudinalement entre le premier collecteur et le second collecteur, ainsi qu'une évacuation de condensat s'étendant longitudinalement le long de la paroi supérieure d'au moins un tube parmi la pluralité de tubes d'échange de chaleur aplatis. L'évacuation de condensat peut comprendre un canal d'évacuation de condensat s'étendant longitudinalement formé dans une paroi supérieure dudit élément tubulaire aplati, et/ou une série de portes d'évacuation de condensat formées dans les ailettes de transfert de chaleur dans une partie de base liée à la surface externe supérieure d'au moins un tube d'échange de chaleur. Les portes d'évacuation de condensat des ailettes de transfert de chaleur adjacentes sont alignées longitudinalement de manière à fournir une série de portes d'évacuation de condensat alignées longitudinalement le long des surfaces externes supérieures des tubes d'échange de chaleur.
PCT/US2007/004993 2007-02-27 2007-02-27 Évaporateur à tube plat multicanaux avec évacuation de condensat améliorée Ceased WO2008105760A2 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
PCT/US2007/004993 WO2008105760A2 (fr) 2007-02-27 2007-02-27 Évaporateur à tube plat multicanaux avec évacuation de condensat améliorée
US12/527,779 US8307669B2 (en) 2007-02-27 2007-02-27 Multi-channel flat tube evaporator with improved condensate drainage
HK10107500.6A HK1141078B (en) 2007-02-27 Multi-channel flat tube evaporator with improved condensate drainage
CN2007800526833A CN101657689B (zh) 2007-02-27 2007-02-27 改进冷凝物排放的多通道扁平管蒸发器
EP07751730A EP2122289A4 (fr) 2007-02-27 2007-02-27 Évaporateur à tube plat multicanaux avec évacuation de condensat améliorée

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2007/004993 WO2008105760A2 (fr) 2007-02-27 2007-02-27 Évaporateur à tube plat multicanaux avec évacuation de condensat améliorée

Publications (2)

Publication Number Publication Date
WO2008105760A2 true WO2008105760A2 (fr) 2008-09-04
WO2008105760A3 WO2008105760A3 (fr) 2008-12-31

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Country Status (4)

Country Link
US (1) US8307669B2 (fr)
EP (1) EP2122289A4 (fr)
CN (1) CN101657689B (fr)
WO (1) WO2008105760A2 (fr)

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US8166776B2 (en) 2007-07-27 2012-05-01 Johnson Controls Technology Company Multichannel heat exchanger
US8439104B2 (en) 2009-10-16 2013-05-14 Johnson Controls Technology Company Multichannel heat exchanger with improved flow distribution
US20110290448A1 (en) * 2010-05-26 2011-12-01 International Business Machines Corporation Dehumidifying cooling apparatus and method for an electronics rack
US9038406B2 (en) * 2010-05-26 2015-05-26 International Business Machines Corporation Dehumidifying cooling apparatus and method for an electronics rack
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US9414519B2 (en) 2010-05-26 2016-08-09 International Business Machines Corporation Dehumidifying cooling apparatus and method for an electronics rack
US10247481B2 (en) 2013-01-28 2019-04-02 Carrier Corporation Multiple tube bank heat exchange unit with manifold assembly
US10337799B2 (en) 2013-11-25 2019-07-02 Carrier Corporation Dual duty microchannel heat exchanger
EP3581868A1 (fr) * 2018-06-15 2019-12-18 Mitsubishi Heavy Industries Thermal Systems, Ltd. Échangeur de chaleur à eau et refroidisseur de gaz

Also Published As

Publication number Publication date
WO2008105760A3 (fr) 2008-12-31
CN101657689B (zh) 2012-09-05
HK1141078A1 (en) 2010-10-29
US20100012307A1 (en) 2010-01-21
US8307669B2 (en) 2012-11-13
EP2122289A4 (fr) 2013-01-09
CN101657689A (zh) 2010-02-24
EP2122289A2 (fr) 2009-11-25

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